JP5724925B2 - pump - Google Patents

Description

  The present invention relates to a pump, and more specifically, to a pump having a feature of reducing impact.

  In this section, the background art related to the present invention is presented, but it does not necessarily correspond to the known art. Some modern internal combustion engines, such as gasoline fueled engines, employ a system called direct injection. Such a direct injection internal combustion engine is controlled in part by a direct injection fuel injection pump that directly injects gasoline into a cylinder. For example, those described in Patent Documents 1 and 2 are known as fuel injection pumps that can be used in a direct injection internal combustion engine.

International Publication No. 2000/047888 Pamphlet Japanese Patent No. 4499951

  Such a direct-injection fuel injection pump using gasoline has sufficient performance to achieve the intended purpose, but there is still room for improvement. One room for such improvement exists in the control of pressure control valves (PCV). In operation, a member inside the pressure control valve collides with a member adjacent to it. Such a collision can cause noise that can be heard by a person several feet (eg, 3 feet, or about 1 meter) away from an operating direct injection fuel injection pump. Therefore, it has been desired to improve the direct injection fuel injection pump in order to reduce the audible noise of the direct injection fuel injection pump.

  This invention is made | formed in view of the said problem, The objective is to provide the pump which suppressed the noise.

  The present invention employs the following technical means to achieve the above object. It should be noted that this section discloses the outline of the present invention and is not comprehensively disclosed over the entire scope of the present invention or all of its features.

  In the present invention, a pump having a stroke for moving fluid is disclosed. The pump has a pump casing that divides the first volume chamber and the second volume chamber, and the fluid moves from the first volume chamber to the second volume chamber during the stroke. The pump also includes a needle that is movably disposed in the first volume chamber and a valve carrier that is slidably disposed in the second volume chamber. The valve carrier includes an internal stopper, and the valve carrier also has an inner chamber partially defined by the internal stopper. The pump further includes a valve slidably disposed in the inner chamber of the valve carrier, and the valve is impacted by the needle in the above-described stroke. Further, the needle also collides with the valve carrier during the above stroke and gives an impact. Further, the valve impacts and impacts the internal stopper during the stroke, when the needle is different from impacting the valve carrier.

  The present invention also discloses a pump having a suction stroke for moving fluid. The pump has a pump casing that partitions the first volume chamber and the second volume chamber, and fluid moves from the first volume chamber to the second volume chamber during the suction stroke. The pump also includes a needle that is movably disposed in the first volume chamber and a valve carrier that is slidably disposed in the second volume chamber. The valve carrier includes an internal stopper, and the valve carrier further includes an inner chamber partially defined by the internal stopper. A sleeve opening is formed in the valve carrier and provides an access passage to the inner chamber. Further, the pump has a fluid passage defined to penetrate the valve carrier, and a valve seat is provided in the fluid passage. The pump further includes a valve slidably disposed in the inner chamber of the valve carrier, and the valve is seated on or off the valve seat to control fluid flow into the inner chamber. I'm going away. The valve operates to partially eject from the sleeve opening. The needle moves toward the valve and the valve carrier during the suction stroke and eventually operates to impact and impact the valve. Further, the needle operates during the intake stroke, after it collides with the valve, pushes the valve into the inner chamber and separates the valve from the valve seat. In addition, the needle operates during the intake stroke to impact the impact by impacting the valve carrier after the valve is moved away from the valve seat. The valve operates during the intake stroke, after the needle collides with the valve carrier, further advances in the inner chamber and collides with the internal stopper to give an impact.

  Furthermore, the present invention discloses a vehicle fuel pump having an intake stroke and a pressurization stroke for moving fuel. The pump has a pump casing that partitions the first volume chamber, the second volume chamber, the third volume chamber, and the fourth volume chamber. The pump also has a needle that is movably disposed in the first volume chamber and that is forced (biased) toward the second volume chamber. The movement of the needle is selectively controlled by a solenoid. The pump also includes a valve carrier that is slidably disposed in the second volume chamber. The valve carrier includes an internal stopper, and the valve carrier further includes an inner chamber partially defined by the internal stopper. A sleeve opening is formed in the valve carrier and provides an access passage leading to the inner chamber. Further, the pump has a first fluid passage defined to penetrate the valve carrier, and a valve seat is provided in the first fluid passage. The second fluid passage is defined so as to penetrate the internal stopper. The pump further includes a valve that is slidably disposed within the inner chamber of the valve carrier, is forced to seat on the valve seat, and partially protrudes from the sleeve opening. The pump also includes a plunger slidably disposed in the third volume chamber and a check valve that controls the flow from the third volume chamber to the fourth volume chamber. The needle moves toward the valve and the valve carrier during the suction stroke and eventually operates to impact and impact the valve. Further, the needle operates during the intake stroke, after it collides with the valve, pushes the valve into the inner chamber and separates the valve from the valve seat. In addition, the needle operates during the intake stroke to impact the impact by impacting the valve carrier after the valve is moved away from the valve seat. The valve operates during the intake stroke, after the needle collides with the valve carrier, further advances in the inner chamber and collides with the internal stopper to give an impact. The plunger is fueled along a flow path from the first volume chamber through the first fluid passage, through the inner chamber, through the second fluid passage, and to the third volume chamber during the intake stroke. To move in the third volume chamber. Furthermore, the check valve operates to prevent fuel flow from the third volume chamber to the fourth volume chamber during the intake stroke. The solenoid operates to energize to prevent needle impact on the valve during the pressurization stroke, thereby leaving the valve seated on the valve seat and the first volume of fuel in the second volume chamber. The flow to the room is obstructed. In addition, the plunger operates to move in the third volume chamber so as to open the check valve during the pressurization stroke and discharge the fluid in the third volume chamber to the fourth volume chamber.

  Further scope of applicability of the present invention will become apparent from the detailed description provided hereinafter. However, the detailed description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the invention in any way. Also, the attached drawings are only for the purpose of illustrating selected embodiments and are not intended to limit the scope of the present invention.

It is a side view of the vehicle carrying the fuel supply system controlled by the control method concerning one embodiment of the present invention. FIG. 2 is a block diagram of the fuel supply system illustrated in FIG. 1, illustrating a fuel injection valve, a common rail, and a direct injection fuel injection pump controlled by a control method according to an embodiment. FIG. 3 is a side view showing a fuel pump module of the fuel supply system of FIG. 2 according to one embodiment. It is sectional drawing which shows the direct injection type fuel injection pump which concerns on one Embodiment. 1 is a cross-sectional view of a direct injection fuel injection pump showing a plunger, a needle, a suction valve, and an associated pump structure in an operating state. 1 is a cross-sectional view of a direct injection fuel injection pump showing a plunger, a needle, a suction valve, and an associated pump structure in an operating state. 1 is a cross-sectional view of a direct injection fuel injection pump showing a plunger, a needle, a suction valve, and an associated pump structure in an operating state. 4 is a graph illustrating different strokes of a direct injection fuel injection pump relative to a cam position, according to one embodiment. It is a figure which shows the various position and contact location of the needle of a direct injection type fuel injection pump, an intake valve, and various physical stopper structures based on one Embodiment. It is a figure which shows the various position and contact location of the needle of a direct injection type fuel injection pump, an intake valve, and various physical stopper structures based on one Embodiment. It is a figure which shows the various position and contact location of the needle of a direct injection type fuel injection pump, an intake valve, and various physical stopper structures based on one Embodiment. It is sectional drawing which shows the direct injection type fuel injection pump which concerns on one Embodiment.

  Hereinafter, exemplary embodiments of the present invention and control methods will be described in detail with reference to FIGS. 1-12 of the accompanying drawings. Note that corresponding reference numerals indicate corresponding parts throughout the drawings.

  With reference to FIGS. 1-3, a vehicle 10, such as an automobile, is illustrated as including an engine 12, a fuel supply line 14, a fuel tank 16, and a fuel pump module 18. The fuel pump module 18 is accommodated in the fuel tank 16 by using a flange. The fuel pump module 18 is immersed or enclosed in liquid fuel in the fuel tank 16 that varies in volume when the fuel tank 16 has liquid fuel. The electric fuel pump 20 in the fuel pump module 18 supplies fuel from the fuel tank 16 to the direct injection type fuel injection pump 22 through the fuel supply pipe 14. The direct injection type fuel injection pump 22 is a high pressure pump. When the liquid fuel reaches the direct injection type fuel injection pump 22, the liquid fuel is further pressurized before being sent toward the common rail 24. A plurality of fuel injectors 26 receives fuel from the common rail 24 for final combustion in the combustion cylinder of the engine 12. FIG. 3 illustrates an example of the fuel pump module 18 disposed in the fuel tank 16. More specifically, the fuel pump module 18 has a fuel pump module flange 28 that will be present on the upper surface of the fuel tank 16 when the fuel pump module 18 is installed in the installed position.

  Still referring to FIG. 3, the fuel pump module 18 includes an electric fuel pump 20. The electric fuel pump 20 sucks fuel from the reservoir 30 and discharges the fuel through a fuel pump check valve 32 and a fuel filter 34 surrounding the electric fuel pump 20. The fuel pump check valve 32 opens according to the fuel pressure from the electric fuel pump 20 and allows the fuel to flow from the upper part of the electric fuel pump 20 to the fuel filter 34. In this way, the fuel pump check valve 32 prevents the fuel from flowing into the electric fuel pump 20 while the fuel is in the opposite direction, that is, for example, when the electric fuel pump 20 is not pumping. Is allowed to be discharged from the electric fuel pump 20. Therefore, the fuel pressure is maintained in the filter 34 disposed around the electric fuel pump 20 in the fuel filter case 36. The fuel is discharged into the filter 34 and pushed out through the filter 34 toward the bottom of the reservoir 30. Accordingly, the fuel passes through the through hole and flows into the pressure regulator 38 disposed in the pressure regulator case 40. The pressure regulator case 40 may be attached to the fuel filter case 36 or may be formed integrally with the fuel filter case 36. The pressure regulator 38 is in fluid communication with the fuel supply pipe 14 via the feed path 42. The pressure regulator 38 adjusts the fuel pressure in the feed path 42 and the fuel supply pipe 14. The fuel sent out from the pressure regulator 38 flows in the feed path 42 toward the flange 28. The flowing fuel represented by the arrow 44 is fuel that is discharged from the electric fuel pump 20 and reaches the engine 12 via the check valve 32.

  In addition to passing the fuel through the feed path 42 at a desired pressure according to the reference set pressure of the pressure regulator 38, the pressure regulator 38 is in excess of that required to maintain the reference pressure. Fresh fuel is circulated back to the reservoir 30. The fuel returned to the reservoir 30 is again sucked by the electric fuel pump 20. The relatively low pressure fuel is also sent from the pressure regulator 38 to a jet pump 45 disposed at or near the bottom of the fuel tank 16 as shown in FIG. The fuel supply path check valve 46 allows the fuel pressure in the supply path 42 to exceed the reference pressure in order to allow fuel to flow from the pressure regulator 38 through the supply path 42 to the fuel supply pipe 14. The valve is adjusted to open according to the fuel pressure in the feed path 42. The pressure required to open the check valve 46 varies depending on, for example, the applied engine.

  The structure of the direct injection type fuel injection pump 22 and the control method associated with the direct injection type fuel injection pump 22 executed by the engine controller or the pump controller 11 will be described with reference to FIG. The direct injection type fuel injection pump 22 has an outer casing 48 (that is, an entire casing or a pump casing). The outer casing 48 defines a plurality of small volume chambers and includes an internal storage chamber 50 that houses various structures and components that operate to pressurize and control the fuel passing through the direct injection fuel injection pump 22. Compartment formation. The outer casing 48 defines a first volume chamber 54, a second volume chamber 62, a third volume chamber 72, and a fourth volume chamber 84 in the inner storage chamber 50, and the pump 22 Fuel (or other liquid) is discharged through each volume chamber 54, 62, 72, 84 in the manner described in detail below.

  Liquid fuel, such as gasoline, flows through the fuel supply line 14. The fuel supply pipe 14 is connected to the inlet 52 of the direct injection fuel injection pump 22, and finally the fuel flowing in accordance with the arrow 44 that is guided there passes through the inlet 52 and enters the first volume chamber 54. A solenoid coil 56, a needle 58, and a needle spring 60 are disposed in the first volume chamber 54. The needle spring 60 can apply a force to the end portion of the needle 58, and the needle 58 is movably disposed in the first volume chamber 54. The spring 60 applies a force to the needle 58 toward the second volume chamber 62 as described below. It should be understood that the force may be applied to the needle 58 by a biasing member other than the spring 60 without departing from the scope of the present invention.

  The suction valve transporter 92 is slidably disposed in the second volume chamber 62, and the suction valve 64 is slidably disposed in the inner chamber 100 of the transporter 92. As shown, the inner chamber 100 is partially defined by an internal stopper 138. The intake valve 64 operates in cooperation with the needle 58 and engages or disengages the valve seat 66 to control the flow of fuel through the direct injection fuel injection pump 22 ( Sit or leave the valve seat 66). The suction valve 64 receives a force in the direction of the first volume chamber 54, that is, in the direction of the needle 58 by the spring 68. The spring 68 is supported by the wall 70 of the internal stopper 138 of the transporter 92. Note that the suction valve 64 may be applied with a force by a bias member other than the spring 68 without departing from the scope of the present invention.

  When the intake valve 64 is separated from the valve seat 66, the fuel can flow into the third volume chamber 72. The third volume chamber 72 is also called a pressurizing chamber 72, and a plunger 74 that pressurizes the fuel to a desired pressure is disposed in the pressurizing chamber 72 so as to be capable of reciprocating. The outer diameter of the plunger 74 allows its movement while providing a sealing property against the inner diameter or the inner surface 76 of the pressurizing chamber 72. The pressure of the fuel output from the pressurizing chamber 72 is set depending on the required pressure of the internal combustion engine to be applied. In order to assist the adjustment of the output fuel pressure, the outlet check valve 78 is seated on or separated from the valve seat 80 according to the spring constant of the spring 82. The check valve 78 is accommodated in the fourth volume chamber 84. In order to further facilitate the pressurization of the fuel in the pressurizing chamber 72, the end 89 of the plunger 74 slides or contacts along the cam crest of the cam 86. The cam 86 is directly or indirectly driven by the rotation of the engine 12. Therefore, the difference in the length of the plunger and the difference in the number of cam ridges affect the fuel pressurization in the pressurization chamber 72.

  With continued reference to FIG. 4, the needle 58 is in contact with the needle guide 88, and the movement of the needle 58 is guided by the needle guide 88. The needle guide 88 has a needle guide end 90 that contacts the needle 58. Further, the needle guide 88 is formed in an annular shape and has an inner diameter that contacts the needle 58.

  The suction valve carrier 92 has an open end surface 94 (that is, an opening of a sleeve). One end of the suction valve 64 is exposed through the sleeve opening of the open end surface 94, and the suction valve 64 can partially protrude. The intake valve carrier 92 has one or more fluid inlet conduits (first fluid passages) 96 and one or more fluid outlet conduits (second fluid passages) 98. These conduits 96 and 98 allow fluid to flow into and out of the inner chamber 100 of the transporter 92. For example, the fluid inlet conduit 96 allows the passage of fluid from the first volume chamber 54 to the inner chamber 100 of the suction valve transporter 92, while the fluid outlet conduit 98 is the inner chamber 100 of the suction valve transporter 92. From the fluid to the inlet 102 of the third volume chamber 72. As a result, the fluid flows into the third volume chamber 72.

  The suction valve transporter 92 is movable in the second volume chamber 62 between a fixed end, that is, a partition wall (first wall) 109 and the damper 108 of the revenue valve transporter 92. The partition wall 109 separates the first volume chamber 54 and the second volume chamber 62. The damper 108 is made of an annular spring or other member capable of damping an impact force, a vibration load, or the like. The damper 108 is disposed between the suction valve carrier 92 and the partition wall 106. An entrance 102 of the third volume chamber 72 is formed in the partition wall 106. As shown in the figure, the damper 108 is outside the suction valve carrier 92 and inside the second volume chamber 62, while the spring 68 serves as an internal spring of the suction valve carrier 92. 92, rather, it is completely contained and surrounded by the intake valve carrier 92.

  As described above, the third volume chamber 72 is a pressurizing chamber, and the fourth volume chamber 84 is an outlet chamber for fluid flowing out of the direct injection fuel injection pump 22. In order to pressurize the fluid in the third volume chamber 72, the plunger 74 moves in a direction entering and exiting the third volume chamber 72, that is, a direction approaching and moving away from the third volume chamber 72. The outlet check valve 78 operates in cooperation with the outlet check valve spring 82 to close or open the fourth volume chamber 84. The outlet check valve spring 82 allows pressurized fluid to flow into the fourth volume chamber 84 and then flow out from the fourth volume chamber 84 via the pump outlet 112 as effluent fuel 114. Therefore, a force is applied to the outlet check valve 78.

  Now, a more detailed control method of the direct injection fuel injection pump 22 according to the present embodiment will be described based on FIGS. 5-7 and also with reference to FIG. The operation of the pump 22 is described in the context of the “stroke” of the pump 22 in the exemplary embodiment shown in FIGS. 5-8.

  For example, the pump 22 has an intake stroke shown in FIG. In the intake stroke, fuel flows into the first volume chamber 54 in accordance with the arrow 44. When the energization of the solenoid coil 56 is cut off and de-energized, and the plunger 74 moves downward (that is, moves away from the pressurizing chamber 72), the plunger 74 moves away from the pressurizing chamber 72. A suction force is generated from the inlet 52 to the pressurizing chamber 72 by the negative pressure sometimes formed. At the same time, when the plunger 74 moves away from the pressurizing chamber 72 according to the arrow 115, the check valve 78 is seated on the valve seat 80 to form a seal. The force of the spring 82 assists the seating of the check valve 78 on the valve seat 80 during the intake stroke of the plunger 74 to draw fluid into the pressurizing chamber 72. The negative pressure generated in the pressurizing chamber 72 also draws the check valve 78 to the valve seat 80. As described above, FIG. 5 shows that the solenoid coil 56 is electrically de-energized, and as a result, the fuel is drawn into the pressurizing chamber 72 by the plunger 74. As shown in FIG. 8, the position of the plunger 74 in the intake stroke of FIG. 5 occurs in the process of decreasing or decreasing the cam lift amount, for example, the position 118 of the curve 116.

  When the solenoid coil 56 is de-energized, the needle spring 60 applies a force to the needle 58 in a direction in which the needle 58 moves away from the solenoid coil 56, thereby moving the needle 58 toward the suction valve 64. . As a result, the needle 58 abuts (contacts and collides) with the distal end surface of the suction valve 64 protruding from the transporter 92 and moves the suction valve 64 inward of the transporter 92 against the bias force applied by the spring 68. Advance. That is, after the initial contact with the suction valve 64, the needle 58 further moves in the direction of the suction valve transporter 92, and finally collides (contacts or contacts) with the end surface 94 of the open end of the transporter 92. . As a result, the needle 58 applies a force to the surface of the suction valve carrier 92 opposite to the damper 108 to compress the damper 108.

  As the spring 68 is compressed, the suction valve 64 moves in the suction valve carrier 92 and moves away from the valve seat 66. Then, the fuel is allowed to flow into the pressurizing chamber 72 through the suction valve 64. The fuel flow (indicated by arrow 44) is facilitated and facilitated by the negative pressure generated by plunger 74 moving downwards according to arrow 115.

  Referring to FIG. 6, a prestroke, also known as a pre-pressurization stroke and a low pressure return stroke, is illustrated, which occurs when the plunger 74 is moved upwardly in the cylinder or sleeve 120 according to arrow 117. . As illustrated in FIG. 6, the pre-stroke phase consists of the initial stage movement in which the cam 86 lifts the plunger 74 (shown in FIG. 4). However, the fuel can flow in the reverse direction through the direct injection fuel injection pump 22 as indicated by the arrow 122 for a short period of time. For this reason, the fuel is not yet pressurized to the injection pressure in the pressurizing chamber 72. FIG. 6 shows a state of pumping when the solenoid coil 56 is in an OFF state or a non-excited state. The plunger 74 first enters the pressurizing chamber 72 immediately after the bottom dead center (BDC) position of the plunger 74. When moving inward, the intake valve 64 is not seated on the valve seat 66 and the fuel flows out of the inlet of the casing, that is, the inlet 52 of the pump, through the direct injection fuel injection pump 22 from the pressurizing chamber 72. . Since the outlet check valve 78 is pressed toward the valve seat 80 by the outlet check valve spring 82, the outlet check valve 78 is seated on the valve seat 80 during the pre-stroke of FIG. As shown in FIG. 8, the position of the plunger 74 in the pre-stroke of FIG. 6 occurs in the process of increasing the cam lift, for example, the position 124 of the curve 116.

  FIG. 7 shows a pressurizing stroke in which the plunger 74 moves further upward, that is, toward the pressurizing chamber 72 according to the arrow 117. When the plunger 74 moves in the sleeve 120, the fuel is pressurized in the pressurizing chamber 72. As illustrated in FIG. 7, the stage of the pressurization stroke raises the plunger 74 toward top dead center (TDC) in relation to the raising ability of the cam 86 (shown in FIG. 4), ie, the ability to move. That is, it consists of the movement of the moving process. When the fuel is pressurized to a pressure that overcomes the spring force of the check valve spring 82, the fuel flows through the direct injection fuel injection pump 22 and flows out of the direct injection fuel injection pump 22 at the pump outlet 128 according to the arrow 126. be able to. Accordingly, the fuel is pressurized in the pressurizing chamber 72 and flows out through the inlet 110 to the outlet chamber 84.

  Thus, FIG. 7 shows that when the solenoid coil 56 is in an ON state or an excited state, the force of the excited solenoid coil 56 attracts the needle 58, thereby compressing the needle spring 60, causing the end surface 130 of the needle 58 to move. A state in which the suction valve 64 is pulled away from contact with the end face 132 is shown. At this time, the spring 68 applies a force to the intake valve 64 so as to be seated on the valve seat 66. This prevents the fuel from flowing back into the first volume chamber 54, i.e., the inlet chamber 54, and instead the fuel flows into the fourth volume chamber 84, i.e., the outlet chamber 84, and flows out from the outlet 112. It is done.

  With continued reference to FIG. 7, as the fuel flows out of the outlet 112, the force of the fuel flow, and / or the associated pressure in the third volume chamber 72, allows the spring 82 to flow out of the outlet 112. In order to allow compression and movement of the check valve 78, the resistance force of the spring 82 against the check valve 78, that is, greater than the compression force. The spring 68 sucks with the wall 70 as a fixed end to prevent fuel from flowing through the fluid inlet conduit 96 when the suction valve 64 is about to close and when the suction valve 64 is pressed against the valve seat 66. A force is applied to the valve 64. Similarly, the spring 82 secures the wall 134 to a fixed end when the check valve 78 is moving away from the valve seat 80 and when it is seated on the valve seat 80 (ie, either opened or closed, respectively). As a result, a force is applied to the check valve 78.

  Thus, FIGS. 5-7 show the position of the plunger 74, the corresponding state of the solenoid coil 56 (eg, the ON state or the OFF state), and the flow of the plunger 74 to the fuel flow in the direct injection fuel injection pump 22, respectively. The influence and effect of the position and the state of the solenoid coil 56 are shown. As shown in FIG. 8, the position of the plunger 74 in the pressurization stroke of FIG. 7 occurs in the process of increasing the cam lift, for example, the position 136 of the curve 116.

  FIGS. 9-11 show the positions of the internal components of the direct injection fuel injection pump 22 in different strokes or stages of operation. FIG. 9 shows the positions of the needle 58 and the suction valve 64 during the pressurization stroke when the solenoid coil 56 is excited as described with reference to FIG. In this situation, the suction valve 64 is seated on the valve seat 66, the solenoid coil 56 is excited, and the needle 58 is attracted to the spring holder 61, and a gap is created between the needle 58 and the suction valve 64. Therefore, noise due to contact between the needle 58 and the suction valve 64 does not occur. This situation occurs when the plunger 74 is approaching the plunger TDC position (see FIG. 7). Since the intake valve 64 is seated on the valve seat 66, no fluid flows through at least the fluid inlet conduit 96 during the pressurization stroke.

  FIG. 10 shows that the current to the solenoid coil 56 is cut off, so that the solenoid coil 56 is de-energized, the needle 58 is not attracted to the spring retainer 61, and the plunger 74 has a downward stroke (for example, a suction stroke). ) Indicates the situation that started. The needle 58 breaks physical contact with the spring holder 61 and moves toward the suction valve 64 by the force of the spring 60 held by the spring holder 61. The spring 60 is disposed between the solenoid coils 56, that is, inside the solenoid coil 56. Thus, the spring 60 applies a force to the needle 58 so that the end face 130 of the needle 58 moves toward the end face 132 of the intake valve 64 and causes a collision. As shown in FIG. 10, audible noise is generated when the needle 58 collides with the intake valve 64. After the needle 58 collides with the suction valve 64, the needle 58 continues to move toward the suction valve carrier 92. When the suction valve 64 moves beyond the end face 94 of the suction valve transporter 92 and enters the region of the suction valve transporter 92 completely and as a whole, the end face 130 of the needle 58 becomes the end face of the suction valve transporter 92. Hits 94. Such a collision also generates audible noise. Moreover, an impact load and vibration are also generated by this collision. As shown in FIG. 10, the impact load or vibration (ie, the first load) is transmitted through the transporter 92 and weakened by the damper 108 as illustrated by arrows 146 and 148. That is, the damper 108 operates as a shock absorber, and alleviates the impact of the collision between the needle 58 and the end face 94 of the suction valve carrier 92. The damper 108 is flexible and may be, for example, a spring or a member that plays a role as a spring for absorbing energy from the suction valve carrier 92.

  FIG. 11 illustrates the continuation of the suction stroke initiated in FIG. 10 where fluid flows from the fluid inlet conduit 96 through the suction valve inner chamber 100 and the fluid outlet conduit 98 into the pressurized chamber 72. Be drawn into. When the suction valve 64 moves away from the valve seat 66, the suction valve 64 advances toward the internal stopper 138 of the suction valve carrier 92 and collides with its end surface 113. The internal stopper 138 is a part of the suction valve carrier 92. The internal stopper 138 is defined as a receptacle for the intake valve spring 68. That is, the inner stopper 138 is surrounded by the wall 144 and has a defined cavity 142. The intake valve spring 68 is disposed in the cavity 142 such that only one end of the intake valve spring 68 protrudes beyond the end surface 113 of the wall 144. When compressed by the intake valve 64, the intake valve spring 68 is compressed against the wall 70 in the cavity 142. As a result, the suction valve spring 68 has no portion protruding beyond the end face 113 of the internal stopper 138 (the whole suction valve spring 68 enters the cavity 142). When the suction valve 64 collides with the end face 113 of the internal stopper 138 placed completely in the region of the suction valve carrier 92, the vibration load or impact load (that is, the second load) generated by the collision is indicated by an arrow. 147 (FIG. 11) is transmitted to the damper 108 via the intake valve carrier 92. The damper 108 operates as a shock absorber, and alleviates the impact of the collision between the suction valve 64 and the end surface 113 of the internal stopper 138 of the suction valve transporter 92. The damper 108 is flexible, for example, a spring, or plays a role as a spring for absorbing energy from the suction valve carrier 92. Therefore, the damper 108 is not provided, and the suction valve carrier 92 exists directly between the second volume chamber 62 and the third volume chamber 72, and the partition wall 106 that divides both chambers is provided. Compared with the collision, according to the configuration of the present embodiment liquid, vibration, impact, and noise are alleviated and reduced.

The method of controlling the pump 22 includes providing a first volume chamber 54 in the outer casing 48 that defines the inlet 52. The method of this embodiment also includes providing a first wall 109 that defines a first opening 53 (FIG. 4) to allow fluid to flow to the intake valve carrier 92. The first volume chamber 54 accommodates a solenoid coil 56, and excitation and non-excitation of the solenoid coil 56 controls the movement of the needle 58. The method of the present embodiment also includes providing a second volume chamber 62 having a suction valve 64 in the outer casing 48. The second volume chamber 62 is disposed next to the first volume chamber 54, and the first opening 53 defines a fluid passage between the first volume chamber 54 and the second volume chamber 62. Furthermore, the method of the present embodiment also includes providing a third volume chamber 72 that opens to the sleeve 120 in the outer casing 48. Sleeve 120 is
It has a cylindrical shape and holds the plunger 74. The method of this embodiment also includes providing a second wall 106 that defines a second opening 102 as a fluid passage between the second volume chamber 62 and the third volume chamber 72. Further, the method of the present embodiment includes a third volume chamber 84 having an outlet check valve 78 and a third opening 110 that defines a third opening 110 between the third volume chamber 72 and the fourth volume chamber 84. It also includes providing a wall 111.

  Although described slightly differently, according to the present embodiment, the pump 22 includes a needle 58, a suction valve 64, and a suction valve carrier 92, and the suction valve 64 is movable in the suction valve carrier 92. Placed in. In order during the operation of the suction stroke of the pump 22, the needle 58 contacts the intake valve 64 and the needle 58 contacts the intake valve carrier 92 (at the contact point 119 in FIG. 10). As a result, the impact is transmitted to the suction valve transporter damper 108 through the suction valve transporter 92 as indicated by arrows 146 and 148. Subsequently, the suction valve 64 comes into contact with the internal stopper 138 of the suction valve carrier 92 (at the contact point 121 in FIG. 11). As a result, the impact is transmitted from the end surface 113 to the suction valve transporter damper 108 through the internal stopper 138 of the suction valve transporter 92 and the remaining portion of the suction valve transporter 92 as indicated by an arrow 147.

  The pump 22 further has an outer casing 48. The outer casing 48 is an outer casing of the pump 22, and defines the first volume chamber 54 and fixes the solenoid coil 56 in the first volume chamber 54. The outer casing 48 defines a second volume chamber 62, and the suction valve transporter 92 is separated from the suction valve transporter damper 108 and the partition wall 109, which is also expressed as a pile, an annular ring, or a holder. And (in between) the second volume chamber 62. The outer casing 48 also defines a third volume chamber 72. At this time, the wall 106 separates the boundary between the second volume chamber 62 and the third volume chamber 72. The suction valve transporter damper 108 is between the suction valve transporter 92 and the wall 106. The suction valve carrier 92 has a first fluid passage (fluid inlet conduit) 96 that allows fluid to flow into the inner chamber 100 of the suction valve carrier 92 from the outside of the suction valve carrier 92. (The fluid also flows in the opposite direction depending on the stroke of the plunger 74.) The suction valve transporter 92 further causes the fluid to flow out of the inner chamber 100 of the suction valve transporter 92 to the outside of the suction valve transporter 92. A second fluid passage (fluid outlet conduit) 98 is also provided. The suction valve 64 controls the passage of fluid from the first fluid passage 96 to the inner chamber 100. The suction valve transporter damper 108 reduces the impact of the needle 58 colliding with the end face 94 of the suction valve transporter 92, the impact of the suction valve 64 impacting the internal stopper 138, and the impact of the needle 58 impacting the suction valve 64. In addition, it is in contact with the intake valve carrier 92 (eg, with spring-like or cantilevered flexibility). The intake valve spring 68 is in the internal stopper 138 of the intake valve carrier 92 and can be compressed from a length beyond the end face 113 of the internal stopper 138 to a length that is coplanar with the end face 113. The plunger 74 is in a third volume chamber 72 defined by the outer casing 48, and the third volume chamber 72 is fluidly connected to the second volume chamber 62. The outlet check valve 78 is disposed in a fourth volume chamber 84 defined by the outer casing 48, and the fourth volume chamber 84 is fluidly connected to the third volume chamber 72.

  The suction valve carrier 92 defines a sleeve 107 (see FIG. 4) in the inner chamber 100 as a fluid reservoir, and the suction valve 64 is partially placed on the sleeve 107 and a part of the end face of the suction valve carrier 92. Jump out of 94. The width (for example, diameter) of the needle 58 is larger than the width (for example, inner diameter) of the opening of the sleeve 107. Accordingly, the suction valve transporter 92 serves as a stopper for the needle 58 (that is, the movement of the needle 58 relative to the transporter 92 is limited). The wall 106 separates the second volume chamber 62 and the third volume chamber 72, and the suction valve transporter damper 108 is placed between the suction valve transporter 92 and the wall 106.

  In another arrangement, the pump 22 has a first volume chamber 54 in the outer casing 48 and the wall 109 defines the first opening 53. The first volume chamber 54 accommodates a solenoid coil 56, and the solenoid coil 56 controls the reciprocation of the needle 58. The pump 22 includes a second volume chamber 62 having a suction valve carrier 92 in the outer casing 48. A movable suction valve 64 is included in the suction valve carrier 92. The first wall 109 defines a first opening 53 and allows fluid to pass between the first volume chamber 54 and the second volume chamber 62. The third volume chamber 72 is defined in the outer casing 48 and opens to the sleeve 120 including the plunger 74. The second wall 106 defines a second opening 102 as a fluid passage between the second volume chamber 62 and the third volume chamber 72. The fourth volume chamber 84 houses the outlet check valve 78, and the third wall 111 defines a third opening 110 between the third volume chamber 72 and the fourth volume chamber. While the pump 22 is operating, the following occurs in sequence: (A) The needle 58 and the suction valve 64 come into contact with each other. (B) The needle 58 and the suction valve carrier 92 are in contact with each other. (C) The suction valve 64 contacts the internal stopper 138 of the suction valve carrier 92.

  Referring to FIGS. 9-11, the following contacts can occur in the following order: (A) The end surface 130 of the needle 58 contacts the end surface 132 of the suction valve 64. (B) The end surface 130 of the needle 58 contacts the end surface 94 of the suction valve carrier 92. (C) The end surface of the suction valve 64 comes into contact with the end surface 113 of the internal stopper 138 of the suction valve carrier 92.

  When the needle 58 contacts the suction valve transporter 92, and subsequently, when the suction valve 64 contacts the end surface 113 of the internal stopper 138 of the suction valve transporter 92, from the suction valve transporter 92 to the suction valve transporter damper 108, It is defined as the vibration path through solid materials. Since two separate collisions occur, one object with a larger mass (eg, the combination of the needle 58 and the intake valve 64 moves together and contacts together as a single unit) However, the noise from the pump 22 can be made smaller than when colliding with the end surface 113 of the internal stopper 138.

  FIG. 12 shows a cross-sectional view of an embodiment according to the present invention. Corresponding reference characters indicate corresponding parts throughout the several views.

  The advantage of this embodiment is that multiple collisions occur in series between parts having a relatively small mass (eg, the needle 58 is connected to the intake valve 64) instead of colliding fewer parts with a larger mass. The direct injection type fuel injection pump 22 so that the end surface 130 of the needle 58 collides with the end surface 94 of the intake valve carrier 92 and the intake valve 64 collides with the end surface 140 of the internal stopper 138 of the intake valve carrier 92. Since the noise level due to the collision is reduced, the operation of the pump 22 can be made quiet overall. Furthermore, the present embodiment can be successfully applied to an engine that operates at any rotational speed.

  The foregoing description of the embodiments has been made for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention. Individual elements or features of a particular embodiment are not limited to that particular embodiment, and are interchangeable and selected where applicable, even if not specifically illustrated or described. May be used in certain embodiments. Further, the above-described embodiment can be modified in various ways. Such variations are not to be regarded as a departure from the invention, and all such modifications are intended to be included within the scope of the invention.

22 Direct Injection Fuel Injection Pump 48 Casing 52 Inlet 54 First Volume Chamber 56 Solenoid Coil 58 Needle (First Valve Member)
60 Spring 62 Second volume chamber 64 Suction valve (second valve member)
66 Valve seat 68 Spring 72 Third volume chamber 74 Plunger 78 Check valve (third valve member)
82 Spring 84 Fourth volume chamber 92 Suction valve carrier 108 Suction valve carrier damper

Claims (20)

A pump (22) having a stroke for moving the fluid,
A pump casing (48) defining a first volume chamber (54) and a second volume chamber (62), wherein fluid flows from the first volume chamber to the second volume during the stroke; Move to the volume chamber,
The pump further
A needle (58) movably disposed in the first volume chamber;
A valve carrier (92) that is movably disposed in the second volume chamber, includes an internal stopper (138), and has an internal chamber (100) partially partitioned by the internal stopper;
A valve (64) movably disposed in the inner chamber of the valve carrier,
The valve is operated so as to be shocked by the needle during the stroke, the needle is operated so as to collide with the valve carrier during the stroke and shock is applied, and the valve further includes: During the stroke, when the needle is different from giving an impact to the valve carrier, the pump operates to collide with the internal stopper and give an impact.   2. The solenoid coil (56) disposed in the first volume chamber, wherein excitation and de-excitation of the solenoid coil selectively cause movement of the needle. Pump.   The pump according to claim 1, further comprising a needle biasing member (60) for applying a force to the needle toward the valve.   Further, the needle operates so as to weaken at least one of a first load caused by impacting the valve carrier and a second load caused by impacting the internal stopper by the valve. The pump according to claim 1, further comprising a valve-carrying damper (108). The pump casing defines the third volume chamber (72),
And a wall (106) separating the boundary between the second volume chamber and the third volume chamber,
The pump according to claim 4, wherein the valve damper is disposed between the valve carrier and the wall.   The pump according to claim 4, wherein the valve damper damper operates to weaken both the first and second loads.   The pump according to claim 1, wherein the valve carrier has at least one fluid passage (96, 98) for the movement of fluid flowing into and out of the inner chamber of the valve carrier.   The at least one fluid passage includes a first fluid passage (96) that allows fluid to flow into the inner chamber from the outside of the valve carrier during the stroke, and the inner chamber from the inner chamber to the inner chamber. The pump according to claim 7, further comprising a second fluid passage (98) that allows fluid to flow out of the fluid. A valve seat (66) formed in the at least one fluid passageway;
A valve (64) selectively seated on and off from the valve seat;
The pump according to claim 7, wherein the flow of fluid through the at least one fluid passage is controlled by seating or separating the valve with respect to the valve seat.   Further, the valve has a valve bias member (68) for applying a bias load to the valve toward a position where the valve is seated on the valve seat. The pump according to claim 9, wherein the valve is moved away from the valve seat.   The valve carrier has a sleeve opening (107) through which the valve protrudes from the valve carrier, and the impact applied by the needle to the valve causes the valve to open the sleeve opening. The pump according to claim 10, wherein the pump is pushed into the inner chamber.   The width of the needle is greater than the width of the sleeve opening so that after impacting the valve and propelling the valve into the sleeve opening and the inner chamber, the needle The pump according to claim 11, wherein the pump collides with the valve carrier and gives an impact. A pump (22) having a suction stroke for moving the fluid,
A pump casing (48) defining a first volume chamber (54) and a second volume chamber (62) is provided, and fluid flows from the first volume chamber to the second volume during the suction stroke. Move to the volume chamber of the
The pump further
A needle (58) movably disposed in the first volume chamber;
An inner chamber (100) that is movably disposed in the second volume chamber, includes an internal stopper (138), and is partially partitioned by the internal stopper, and a sleeve opening (107) that provides a passage leading to the inner chamber. ), A valve carrier (92) having
Fluid passages (96, 98) defined to penetrate the valve carrier and forming a valve seat (66);
A valve (64) movably disposed in the inner chamber of the valve carrier so as to be seated or separated from the valve seat in order to control the flow of fluid to the inner chamber;
The valve operates to partially protrude from the sleeve opening;
The needle moves toward the valve and the valve carrier during the suction stroke, and eventually operates to impact and impact the valve;
Further, the needle operates during the suction stroke, after the valve collides with the valve, to push the valve into the inner chamber and to separate the valve from the valve seat;
And the needle operates to impact and impact the valve carrier during the suction stroke, after the valve is separated from the valve seat, and
The valve is operated during the suction stroke so as to further advance in the inner chamber after the needle collides with the valve carrier and collide with the internal stopper to give an impact. To pump.   Further, the valve operates so as to weaken both the first load caused by the impact of the needle on the valve carrier and the second load caused by the impact of the valve on the internal stopper. 14. A pump according to claim 13, comprising a transporter damper (108).   Furthermore, the valve has a valve bias member (68) for applying a bias load to the valve toward a position where the valve is seated on the valve seat, and the impact applied by the needle to the valve causes the valve to be biased. 14. The pump according to claim 13, wherein the valve moves away from the valve seat.   The width of the needle is greater than the width of the sleeve opening so that after impacting the valve and propelling the valve into the sleeve opening and the inner chamber, the needle The pump according to claim 13, wherein the pump collides with the valve carrier and gives an impact. The pump casing defines a third volume chamber (72) fluidly connected to the second volume chamber;
A plunger (74) movably disposed in the third volume chamber;
The plunger passes through the third volumetric chamber so that the fluid flows from the first volumetric chamber through the second volumetric chamber and into the third volumetric chamber during the suction stroke. The pump according to claim 13, wherein the pump moves. The pump casing defines a fourth volume chamber (84) fluidly connected to the third volume chamber,
The pump according to claim 17, further comprising a check valve (78) for controlling a flow of fluid from the third volume chamber to the fourth volume chamber. The pump has a pressurization stroke in which the solenoid coil (56) operates to excite the needle to impinge on the valve so that the valve is seated in the valve seat. The fuel in the second volume chamber is prevented from flowing into the first volume chamber,
The plunger operates to move in the third volume chamber so as to open the check valve and discharge the fluid in the third volume chamber to the fourth volume chamber during the pressurization stroke. The pump according to claim 18. A vehicle fuel pump (22) having a suction stroke and a pressure stroke for moving fuel,
A pump casing (48) defining a first volume chamber (54), a second volume chamber (62), a third volume chamber (72), and a fourth volume chamber (84);
A needle (58) movably disposed in the first volume chamber, a force applied to the second volume chamber, the movement of which is selectively controlled by a solenoid coil (56);
An inner chamber (100) that is movably disposed in the second volume chamber, includes an internal stopper (138), and is partially partitioned by the internal stopper, and a sleeve opening (107) that provides a passage leading to the inner chamber. ), A valve carrier (92) having
A first fluid passageway (96) defined to penetrate the valve carrier and forming a valve seat (66);
A second fluid passage (98) defined to penetrate the internal stopper;
A valve (64) movably disposed in the inner chamber, seated on the valve seat and applied with force to partially protrude from the sleeve opening;
A plunger (74) movably disposed in the third volume chamber;
A check valve (78) for controlling the flow of fluid from the third volume chamber to the fourth volume chamber,
The needle moves toward the valve and the valve carrier during the suction stroke, and eventually operates to impact and impact the valve;
Further, the needle operates during the suction stroke, after the valve collides with the valve, to push the valve into the inner chamber and to separate the valve from the valve seat;
Further, the needle operates during the suction stroke, and after the valve is separated from the valve seat, the needle collides with the valve carrier to give an impact,
The valve operates during the intake stroke, after the needle collides with the valve carrier, further proceeds in the inner chamber and collides with the internal stopper to give an impact;
The plunger passes from the first volume chamber through the first fluid passage, through the inner chamber, through the second fluid passage, and into the third volume chamber during the suction stroke. Operate to move in the third volume chamber to draw fuel along the flow path to
The check valve operates to prevent fuel flow from the third volume chamber to the fourth volume chamber during the intake stroke;
The solenoid coil operates to excite in the pressurization stroke to prevent a needle from colliding with the valve, so that the valve remains seated on the valve seat and the second volume The indoor fuel is prevented from flowing into the first volume chamber,
The plunger operates to move in the third volume chamber so as to open the check valve and discharge the fluid in the third volume chamber to the fourth volume chamber during the pressurization stroke. Vehicle fuel pump.

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